EP0399277A2 - Hydraulischer Motor mit Kupplungsbremse - Google Patents

Hydraulischer Motor mit Kupplungsbremse Download PDF

Info

Publication number
EP0399277A2
EP0399277A2 EP90108574A EP90108574A EP0399277A2 EP 0399277 A2 EP0399277 A2 EP 0399277A2 EP 90108574 A EP90108574 A EP 90108574A EP 90108574 A EP90108574 A EP 90108574A EP 0399277 A2 EP0399277 A2 EP 0399277A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic motor
motor according
clutch
shell
joint
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP90108574A
Other languages
English (en)
French (fr)
Other versions
EP0399277A3 (de
EP0399277B1 (de
Inventor
Corrado Brevini
Maurizio Brevini
Mauro Marani
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SAM Hydraulik SpA
Original Assignee
SAM Hydraulik SpA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SAM Hydraulik SpA filed Critical SAM Hydraulik SpA
Publication of EP0399277A2 publication Critical patent/EP0399277A2/de
Publication of EP0399277A3 publication Critical patent/EP0399277A3/de
Application granted granted Critical
Publication of EP0399277B1 publication Critical patent/EP0399277B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
    • F16D67/02—Clutch-brake combinations
    • F16D67/04—Clutch-brake combinations fluid actuated

Definitions

  • the present invention relates to a hydraulic motor with clutch brake of the type defined in the pre-characterizing part of claim 1.
  • the clutch brake is arranged on the output shaft of the motor itself.
  • This arrangement entails problems mostly regarding the bulk and installation of the motor.
  • the technical aim of the present invention is therefore to provide a motor of the above kind which is structurally simple and in particular has a reduced axial bulk.
  • an object of the invention is to provide a hydraulic motor which has a braking torque which is significantly greater than that of known types.
  • the motor comprises an elongated casing 1 which is externally shaped and is internally crossed by a cavity 2 which is coaxial to the longitudinal axis A.
  • a shaft 3 is accommodated in the front part of cavity 2, protrudes from the casing and is rotatably supported on a pair of bearings 4.
  • the shaft 3 has, at the end inside the cavity 2, an internal toothed seat 5 which is engaged by a toothed portion 6 of a substantially cylindrical half-joint 7.
  • the half-joint is not coaxial to the shaft 3 but is inclined by a small angle along the axis B. In this manner, when the joint rotates as described hereafter, the axis B traces a cone the apex whereof is on the axis A.
  • the half-joint 7 traverses openings provided in some elements accommodated in the cavity 2, such as: a fixed distribution element 8 which is sealingly centered in the cavity 2 by shoulders 9, a rotating distributor 10 and a manifold 11 which is traversed by the ducts for the working fluid, in particular pressurized oil, which is fed through the delivery duct 12 and recovered through the discharge duct 13.
  • a fixed distribution element 8 which is sealingly centered in the cavity 2 by shoulders 9
  • a rotating distributor 10 and a manifold 11 which is traversed by the ducts for the working fluid, in particular pressurized oil, which is fed through the delivery duct 12 and recovered through the discharge duct 13.
  • Parts 7-11 are not described further since they are fully conventional in hydraulic motors.
  • the half-joint 7 On the opposite side to that of the toothed portion 6, the half-joint 7 has a toothed portion 14 which is adapted to couple to a volumetric element generally indicated by the reference numeral 15.
  • Said volumetric element is composed of a stator 16 which has an internal cavity 17 in the shape of a star, for example with seven points, and of a star-shaped rotor 18, for example with six points, accommodated and rolling inside the cavity 17.
  • Stator 16 and rotor 18 define chambers 19 into which the pressurized oil is caused to flow through the distributor 10.
  • the star-shaped rotor 18 has a central toothed hole 20 rotationally engaging the toothed portion 14 of the half-­joint 7.
  • a cylindrical pivot 21 extends axially from the toothed portion 14 and protrudes from the volumetric element 15.
  • the stator is clamped between the manifold 11 and a brake shell 22 which is coupled to the casing 1 by means of a plurality of stud bolts 23.
  • the shell 22 (see figure 3) encloses a coaxial cavity 24 which is rearwardly closed by a cover 25 which is shaped internally so as to form a cylindrical extension 26 in which two diametrical dead holes 27 are frontally provided to acommodate cylindrical dowels 28.
  • Said cylindrical dowels 28 rotationally retain a cap 29 which is centered on the extension 26 and has a coaxial seat 30, into which there lead two holes 31 for the respective dowels 28, and a central opening 32 for discharging oil toward a duct 33 formed in the cover 25.
  • a ball bearing 34 is arranged in the seat 30 and rotationally supports the rear part of a traction body, generally indicated by the reference numeral 35.
  • the body 35 has the shape of a cup which is directed, with its larger-diameter end, toward the volumetric element 15, and is externally provided with a rolling track 36 for a roller case 37 for supporting the body 35 in the cavity 24 and a shoulder 38 for the bearing 34.
  • a cavity 39 is provided in the face of the body 35 which is directed toward the volumetric element 15; said cavity has a diametrically elongated rectangular cross section, with rounded ends, and slidably accommodates a sliding pad 40 in which the pivot 21 of the half-joint 7 is inserted.
  • Ducts 41, 42 and 43 are provided in the body 35 and connect the cavity 39 and the cavity 24.
  • the region comprised between the shoulder 38 and the track 36 has a series of longitudinal grooves 44 which are angularly distributed on the circumference.
  • Two adjacent clutch disks and 46 surround said region and two rings 47, 48 are arranged at both sides of the disk 46 and are provided with teeth which slidably engage the grooves 44, thus coupling the rings 47, 48 to the body 35 to rotate therewith.
  • the disks 45, 46 have peripheral notches 49 which are traversed by the bolts 23 so as to prevent the rotation of said disks but allow their axial sliding.
  • the ring 48 is interposed between the disk 46 and the planar front edge surface 50 of the cap 29.
  • Radial channels 51 are provided in the cap 29 and connect the cavity 52, internally defined by the cap 29, to the cavity 24 which is external thereto.
  • An annular channel-like seat 53 is provided in the cover 25, being internally delimited by the outer surface of the extension 26 and externally delimited by a wall 54.
  • the annular head of a piston 55 is sealingly slidable in the seat 53; said piston has a skirt 56 which embraces the cap 29 and extends toward the disk 46.
  • Axial dowels 57 are interposed between the front edge of the skirt 56 and the disk 45, are angularly spaced and pass through the disk 46.
  • the piston 55 has an annular chamfer; when the piston head is in contact with the bottom of the seat 53, said chamfer defines an annular chamber 58 which is constantly connected to a duct 59 which is connected to the pressurized oil feed.
  • the shell 22 On the side of the volumetric element 15, the shell 22 has an internal expansion 60 in which axial recesses 61 are provided; said recesses are open toward the disk 45 and are angularly spaced. Respective compression springs 62 are accommodated in the recesses 61 and act against the disk 45, keeping it resting on the piston through the dowels 57.
  • the operation of the motor is as follows.
  • the motor is fed with pressurized oil through the ducts 12 and 59. Pressure suitable to rotate the half-joint 7, which transmits its motion to the output shaft 3, is created in the internal chambers of the volumetric element 15.
  • the annular chamber 58 of the piston 55 is filled by the pressurized oil, so that the piston 55 is pushed against the disk 45 in contrast with the springs 62. In this manner, the disk 45 is spaced from the other disk 46, allowing release of the clutch and free rotation of the body 35 and of the rings 47, 48 associated therewith.
  • the supply of pressurized oil is removed and the annular chamber 58 is connected to the discharge.
  • the braking of the body 35 in turn causes that of the half-joint 7 and of the shaft 3.
  • a substantial advantage of the present invention is constituted by the fact that the described motor is brought to a locked condition if motor oil pressure is absent. This allows to provide a mechanical-action safety brake when the motor is installed as a propulsion element in vehicles, lifting devices and the like.
  • Another advantage is to be found in the compact structure of the motor, in which the braking element has a modest bulk which does not hinder the application of the motor.
  • a further advantage is constituted by the fact that the brake acts on the half-joint and the braking effect is thus multiplied with respect to brakes which act on the output shaft.
  • a further advantage of the invention is its applicability to currently existing hydraulic motors, since the brake constitutes an additional module which requires no modification of the motor.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Motors (AREA)
  • Braking Arrangements (AREA)
EP90108574A 1989-05-22 1990-05-07 Hydraulischer Motor mit Kupplungsbremse Expired - Lifetime EP0399277B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT347489 1989-05-22
IT8903474A IT1234077B (it) 1989-05-22 1989-05-22 Motore idraulico con freno a frizione a trascinamento multiplicato

Publications (3)

Publication Number Publication Date
EP0399277A2 true EP0399277A2 (de) 1990-11-28
EP0399277A3 EP0399277A3 (de) 1991-02-27
EP0399277B1 EP0399277B1 (de) 1994-11-02

Family

ID=11108058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90108574A Expired - Lifetime EP0399277B1 (de) 1989-05-22 1990-05-07 Hydraulischer Motor mit Kupplungsbremse

Country Status (4)

Country Link
EP (1) EP0399277B1 (de)
DE (1) DE69013751T2 (de)
DK (1) DK0399277T3 (de)
IT (1) IT1234077B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117083469A (zh) * 2021-05-21 2023-11-17 丹佛斯有限公司 包括具有摩擦制动器的摆线式马达的液压驱动器装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19520402C2 (de) * 1995-06-08 1999-01-21 Danfoss As Hydraulischer Kreiskolbenmotor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3863038A (en) * 1973-06-26 1975-01-28 Lambert & Brake Corp Disc brake
US4128145A (en) * 1977-08-31 1978-12-05 Lambert Brake Corporation Combination failsafe brake and one-way clutch
FI72782C (fi) * 1985-03-20 1987-07-10 Valmet Oy Hydraulisk motor.
HU203704B (en) * 1987-09-28 1991-09-30 Magyar Vagon Es Gepgyar Epicyclic-gear carriage

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117083469A (zh) * 2021-05-21 2023-11-17 丹佛斯有限公司 包括具有摩擦制动器的摆线式马达的液压驱动器装置
CN117083469B (zh) * 2021-05-21 2026-03-24 丹佛斯有限公司 包括具有摩擦制动器的摆线式马达的液压驱动器装置

Also Published As

Publication number Publication date
DE69013751T2 (de) 1995-03-16
DK0399277T3 (da) 1995-04-03
EP0399277A3 (de) 1991-02-27
EP0399277B1 (de) 1994-11-02
DE69013751D1 (de) 1994-12-08
IT1234077B (it) 1992-04-29
IT8903474A0 (it) 1989-05-22

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